EP3266538A1 - Piston for a die-casting maching - Google Patents
Piston for a die-casting maching Download PDFInfo
- Publication number
- EP3266538A1 EP3266538A1 EP17179726.9A EP17179726A EP3266538A1 EP 3266538 A1 EP3266538 A1 EP 3266538A1 EP 17179726 A EP17179726 A EP 17179726A EP 3266538 A1 EP3266538 A1 EP 3266538A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- stem
- lubrication
- sealing ring
- duct
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000004512 die casting Methods 0.000 title claims abstract description 13
- 238000007789 sealing Methods 0.000 claims abstract description 63
- 238000005461 lubrication Methods 0.000 claims abstract description 46
- 239000000314 lubricant Substances 0.000 claims description 31
- 229910052751 metal Inorganic materials 0.000 claims description 18
- 239000002184 metal Substances 0.000 claims description 18
- 238000001816 cooling Methods 0.000 claims description 13
- 230000008878 coupling Effects 0.000 claims description 10
- 238000010168 coupling process Methods 0.000 claims description 10
- 238000005859 coupling reaction Methods 0.000 claims description 10
- 239000012809 cooling fluid Substances 0.000 claims description 7
- 238000009826 distribution Methods 0.000 claims description 7
- 239000007788 liquid Substances 0.000 claims description 5
- 230000000149 penetrating effect Effects 0.000 claims description 4
- 230000004941 influx Effects 0.000 claims 1
- 229910001338 liquidmetal Inorganic materials 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000001050 lubricating effect Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 238000005266 casting Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- -1 e.g. Inorganic materials 0.000 description 1
- 239000003517 fume Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 238000007711 solidification Methods 0.000 description 1
- 230000008023 solidification Effects 0.000 description 1
- 230000008719 thickening Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J1/00—Pistons; Trunk pistons; Plungers
- F16J1/08—Constructional features providing for lubrication
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B22—CASTING; POWDER METALLURGY
- B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
- B22D17/00—Pressure die casting or injection die casting, i.e. casting in which the metal is forced into a mould under high pressure
- B22D17/20—Accessories: Details
- B22D17/2015—Means for forcing the molten metal into the die
- B22D17/203—Injection pistons
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B22—CASTING; POWDER METALLURGY
- B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
- B22D17/00—Pressure die casting or injection die casting, i.e. casting in which the metal is forced into a mould under high pressure
- B22D17/20—Accessories: Details
- B22D17/2015—Means for forcing the molten metal into the die
- B22D17/2038—Heating, cooling or lubricating the injection unit
Definitions
- the object of the present invention is a piston for a die-casting machine, in particular for a cold chamber die-casting machine.
- the present invention refers to a piston with a lubrication circuit adapted to facilitate the sliding of the piston in a container of molten metal of a press for such die-casting machine.
- a piston for a die-casting machine comprises a stem and a piston head having a side wall with at least one sealing area suitable to provide a seal on the wall of the container of the press. Pistons further provided with a lubrication circuit are already known.
- a lubrication duct is made in the stem that branches into a series of holes that flow into the bushing. The lubricant is sprayed toward the head through a plurality of nozzles of the bushing.
- the lubricant Since the lubricant is injected by the lubrication nozzles into an area which, being distant from the piston head, does not undergo the same cooling as the head, the lubricant undergoes a phase change to a gaseous state, losing efficiency and generating fumes that must be aspirated.
- pistons having lubrication holes leading to the vicinity of the head in the sealing area with the container have been proposed.
- Examples of such pistons are described in DE3913494A1 , JP2009279645A , DE29721722U1 , JP2010269319A .
- these embodiments of pistons have proved to be unsatisfactory, particularly because of the fact that the terminal section of the lubrication ducts, open over the piston's sealing surface, is quickly blocked by the metal that in the liquid state is able to penetrate between the piston and the container and solidifies to form a sheet that covers the lubrication duct.
- the piston with the lubricating bushing is complex to construct and requires frequent maintenance, especially to remedy the breakage or obstruction of the tubes and the lubrication nozzles.
- the object of the present invention is to propose a piston for a die-casting machine to overcome the drawbacks mentioned above with respect to the pistons according to the prior art.
- the press comprises a container 400 wherein the piston 1; 500; 700, or at least one of its terminal parts for pushing the molten metal, is housed slidably.
- the container 400 has, in its upper part and at its end, a loading hole for molten metal, e.g., aluminum.
- the container 400 has slits 402 to which correspond starting points of casting branches that flow into a die.
- the piston 1; 500; 700 is thus axially slidable inside the container 400 to push the metal fed through the loading hole into the casting branches and then into the die.
- the piston 1; 500; 700 comprises a stem 10; 510; 710 extending between a proximal end 11, either rearward with respect to the piston feed direction in the container and a distal end 12; 512; 712, or forward, along a piston axis X.
- the piston 1; 500 terminates with a piston head 50; 550; 750 extending from the distal end of the stem and has a side wall with at least one sealing area 52; 552; 752 suitable to form a seal on the wall of said container 400 of the press.
- the piston 1; 500; 700 is provided with a lubrication circuit adapted to facilitate the sliding of the piston in the container 400.
- Said lubrication circuit comprises first lubrication ducts 14, 16, 18 made in the stem 10; 510; 710 and terminating at the distal end 12; 512; 712 of said stem, and second ducts 20 made in the piston head 50; 550; 750, communicating fluidically with said first ducts and flowing into the side wall corresponding at least to said sealing area 52; 552; 752.
- the first lubrication ducts comprise a feed duct 14 extending longitudinally from a lubricant inlet hole 15 and branching into at least two distribution ducts 18 angularly equidistant from the piston axis X.
- the second lubrication ducts 20 are a continuation of said distribution ducts 18.
- the terminal end of each distribution duct 18 is in direct communication with the initial end of a corresponding second lubrication duct 20.
- the inlet hole 15 for the lubricant is made near the proximal end 11 of the stem 10.
- the feed duct 14 thus extends almost over the entire length of the stem, parallel to the piston axis X and lateral with respect to an axial cooling duct, which will be described below, ending near the distal end 12.
- the distribution ducts 18, made in the distal end portion 12 of the stem 10 extend parallel to the piston axis X.
- the feed duct 14 and the distribution ducts 18 are connected to each other by branching ducts 16 extending from the end of the feed duct 14 in a transverse direction with respect to the piston axis X.
- the piston head 50; 550; 750 has at least one sealing ring 60 housed in a respective ring seat 62.
- Examples of piston heads with sealing ring to which the teaching of the present invention may be applied are described in WO2007116426A1 and WO2009125437A1 in the name of the same applicant.
- the ring seat 62 is formed by an annular recess made in the lateral surface of the piston head. Said ring seat 62 is radially delimited by a bottom 62' and axially at least by a rear edge 62a, preferably also by a front edge 62b located near the front face 602 of the piston head.
- the bottom of the sealing ring seat 62 may advantageously be connected to the front surface 602 of the piston head through connecting channels 604 so that the molten metal present in the container may flow under the ring and, solidifying, create a progressive thickening that causes the ring to enlarge radially, compensating for its wear and ensuring the sealing effect over time.
- the sealing ring 60 has a longitudinal gap 60', e.g., in the form of a step, which allows it to expand radially.
- the second lubrication ducts 20 flow at least into the ring seat 62 below the same.
- the sealing ring is closed. Therefore, said second ducts 20 are covered, and thus protected, by the sealing ring 60 against possible obstructions by the metal that should penetrate between the piston and the container 400.
- the pressurized lubricant is then forced to infiltrate under the sealing ring and out of the piston through the gaps between the sealing ring 60 and the piston head and/or through the longitudinal slit 60' of the sealing ring 60.
- the pressurized lubricant is forced to flow out of the piston through the gaps between the sealing ring 60 and the edges 62a, 62b of the ring seat 62.
- the sealing ring 60 is housed with some play in the respective ring seat 62. 'Housed with play' is intended to mean that the sealing ring 60 is not engaged in a forced manner in the respective ring seat 62 but rather that between the sealing ring 60 and each edge 62a, 62b of the ring seat 62 there is a certain and calibrated gap, e.g., 0.1 mm or less.
- the pressurized lubricant e.g., at 200 bar, may pass between the sealing ring 60 and the edges 62a, 62b of the ring seat 62, while the metal, even if when in liquid state, may not pass.
- the lubricant flowing out from the gaps between the ring and the edges of the seat, acts precisely in the contact area between the piston and the inner surface of the container, i.e. the area of the sealing ring 60; moreover, flowing onto the bottom of the ring seat 62, the lubricant contributes to the radial expansion of the ring when the same begins to wear out.
- the sealing ring 60 and the ring seat 62 have interlocking or complementary coupling portions 606, 608 providing a kind of labyrinth that prevents liquid metal from penetrating under the sealing ring 60 and - during cooling and solidification - reaching the portion of the ring seat 62 comprised between said interlocking coupling portions and the rear edge 62a of the seat 62.
- the liquid metal that reaches the ring seat 62 through the connecting channels 604 is forced to solidify in the front portion of the ring seat 62 between said labyrinth and the front edge 62b (or, if said front edge 62b is not provided, between the labyrinth and the front surface 602 of the piston head).
- said interlocking coupling portions comprise one or a pair of annular ribs 606 extending from the bottom 62' of the ring seat 62 and corresponding annular grooves 608 made in the inner wall of the sealing ring 60.
- the bottom 62' of the ring seat 62 is grooved by an annular groove 606 wherein a rib 608 engages extending from the inner wall of the sealing ring 60.
- an annular channel 610 is made, suitable to receive the metal coming from the connection channel 604.
- Figure 18a shows schematically the deposit of metal M in the front portion of the ring seat 62, under the sealing ring 60, and particularly in the annular channel 610.
- the second lubrication duct 20 which flows under the sealing ring flows into the rear portion of the ring seat 62 between the interlocking coupling portions 606, 608 and the rear edge 62a of the ring seat 62.
- said second duct 20 is protected, by means of the labyrinth formed by the interlocking coupling portions, from any obstruction caused by the penetration of the liquid metal under the sealing ring 60.
- the lubricant has a density and a pressure making it able to creep between the interlocking coupling portions 606, 608 and to reach the front gap between the sealing ring and the front edge 62b, although most of the lubricant flows out through the gap between the ring and the rear edge 62a, finding no obstacle in this case.
- the amount of lubricant necessary to ensure the proper sliding of the piston is considerably less than that used in the pistons of the prior art, where the lubricant fails to reach the area of the sealing ring.
- the second ducts 20 have a first section 20' parallel to the piston axis X and at least a second radial section 20" flowing at least in the ring seat 62.
- the piston head 50; 550; 750 is removably connected to the stem 10; 510; 710. Between the stem and the head there are provided sealed fluidic connection means 4; 560 between the first lubrication ducts 14, 16, 18 and the second lubrication ducts 20.
- the distal end 12 of the stem 10 is flanged so as to allow an axial juxtaposition between the stem 10 and the piston head 50.
- the sealed fluidic connection means comprise connection bushings 4, each inserted with calibrated interference half in a terminal section of a first lubrication duct 18 and the other half in the initial section of a second lubrication duct 20.
- Each of said halves is fitted with an annular sealing element 61.
- the flanged distal end 12 of the stem 10 and the adjacent end of the piston head 50 are connected by means of screws 12' (shown in figure 17b ).
- screws 12' shown in figure 17b .
- a plurality of radial recesses 22 are formed, for example, angularly equidistant and semicircular, which allow access to corresponding screw holes 24 made in said flanged distal end 12, parallel to the piston axis X, and facing corresponding screw holes 24'-visible in the view of figure 17b - made in the piston head 50.
- the piston according to the embodiment illustrated in figures 16-18 has a structure similar to the one described for the piston of figures 1-15 and differs from the latter only in having a single first lubrication duct 14 extending into the stem 10 and a single second lubrication duct 20 aligned with the first lubrication duct 14 extending into the piston head and comprising, as described above, a first longitudinal section 20' and a second radial section 20" flowing into the ring seat 62.
- the piston 1; 500 is suitable for use in cold chamber die-casting machines.
- a cooling circuit is made, suitable to circulate a cooling fluid inside the piston head.
- the piston head 50 comprises a hollow outer body 64 fitted, e.g., in the form of a cap, on an axial support pin 66; 766.
- said axial support pin 66 has a proximal or rear end 67, engaging in a corresponding axial recess 68 made in the distal end 12 of the stem 10.
- the outer hollow body 64 and the pin 66 there is no play, at least between the respective side walls.
- the outer hollow body 64 cannot move radially with respect to pin 66.
- the proximal end 67 of the pin 66 is inserted with calibrated interference, i.e. without play, in the corresponding axial recess 68.
- Such a solution allows, together with the screwing of the head onto the stem by means of screws distributed along a circular crown, to achieve and maintain over time a perfect coaxiality between the piston head and the stem.
- the support pin 66 partially penetrating the inside of the stem, acts as a means of guidance and axial support for the piston head 50.
- the stem 10 and the pin 66 have respective and aligned axial cooling holes 70, 72 wherein a delivery tube 74 for a cooling fluid is inserted.
- Said delivery tube 74 communicates with the outside through an inlet hole 80 for the cooling fluid, e.g., made radially in the stem near the distal end 12, and flows onto the front surface 76 of the axial pin 66.
- Said front surface 76 is in fluidic communication, e.g., through a plurality of helical ducts 77, with a spiral cooling channel 78 formed in the outer lateral surface of the axial pin 66.
- Said spiral cooling channel 78 then circulates the cooling fluid around and over the entire outer surface of the axial pin 66 in contact with the outer hollow body 76, cooling it down.
- the cooling channel 78 flows into a return duct 82 communicating with an outlet hole 84 for the cooling fluid, made in the stem.
- said return duct 82 is formed by an annular space between the axial cooling hole 70, 72 and the delivery tube 74 of the cooling fluid.
- the return duct 82 communicates with the spiral cooling channel 78 through one or more radial holes 83 made in the axial pin 66.
- the longitudinal lubrication holes 14 and cooling holes 70 made in the stem 10 are obtained by machining carried out on the rear side of the stem 10. Therefore, in order to close such holes on said side, the proximal end 11 of the stem 10 comprises a cap 90.
- sealed fluidic connection means comprise ball joints 560, each having a first spherical end 561 inserted in a terminal portion of a respective first lubrication duct 14 and a second spherical end 562 inserted in an initial section of a respective second lubrication duct 20, each of said spherical ends being provided with an annular sealing element.
- the piston head 550 is held in contact with the stem 510 by means of a connecting cap 570 fixed to the stem.
- said connecting cap 570 has an engagement end portion 572 at the front which forms an undercut wherein a rear step-shaped portion 574 of the piston head 550 engages.
- the piston head 750 is connected to the stem 710 via an articulated joint 800.
- Said articulated joint 800 allows the head 750 to make deviations of a few degrees with respect to the piston axis X, and hence with respect to the stem 710, e.g., to allow it to slide into a non-perfectly rectilinear container 400.
- the articulated joint 800 has a rear portion 810 coupled to the stem 810 and a spherical head 814 whereon the piston head 750 is assembled.
- the rear portion 810 is fixed axially and radially to the stem 710, e.g., by means of radial blocks 812.
- the piston head 750 For its assembly on the spherical head 814, the piston head 750 comprises a rear flange 820 surrounding the rear portion of the spherical head 814 and which is removably secured, e.g., by means of screws, to a rear portion of the pin 766 surrounding the front portion of the spherical head 814.
- the rear flange 820, and hence the entire piston head 750 is angularly fixed to the articulated joint 800, i.e. it is prevented from rotating about the piston axis X, e.g., by means of a spline 816.
- the second lubrication duct 20, and in particular the end section 20 is always turned in the desired direction, normally upwards.
- the piston is thus lubricated by the lubricant running from top to bottom; moreover, the metal in the liquid state is less likely to solidify on the upper, hotter part of the piston.
- the piston head 750 being spaced from the stem 710, the first lubrication duct 14, made in the stem 710, is fluidically connected to the second lubrication duct 20, made in the piston head 750, by means of a connecting tube 714.
- said connecting tube 714 has a spiral shape or is, in any case, suitable to allow displacements of the piston head 750 with respect to the stem 710.
- the portions of the second lubrication duct 20 made in the rear flange 820, in the pin 766, and in the hollow body 64 are connected to each other through the connection bushings 4.
- At least one non-return valve 5 adapted to ensure the unidirectionality of the flow of lubricant from the stem to the piston head.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
- Compressor (AREA)
- Injection Moulding Of Plastics Or The Like (AREA)
- Sealing Devices (AREA)
- Extrusion Moulding Of Plastics Or The Like (AREA)
Abstract
Description
- The object of the present invention is a piston for a die-casting machine, in particular for a cold chamber die-casting machine. In particular, the present invention refers to a piston with a lubrication circuit adapted to facilitate the sliding of the piston in a container of molten metal of a press for such die-casting machine.
- According to the preamble of
claim 1, a piston for a die-casting machine comprises a stem and a piston head having a side wall with at least one sealing area suitable to provide a seal on the wall of the container of the press. Pistons further provided with a lubrication circuit are already known. - In particular, making a piston with a lubricating bushing placed around the stem in the rearward position relative to the head, so as not to interfere with the sealing action of the head on the walls of the container, is known. A lubrication duct is made in the stem that branches into a series of holes that flow into the bushing. The lubricant is sprayed toward the head through a plurality of nozzles of the bushing.
- Such a solution has made it possible to lubricate the piston even during operation and not only at the start of operation, as had occurred previously; however, some limitations or drawbacks still exist.
- In particular, most of the lubrication effect takes place at a distance from the piston head, and especially at a distance from the friction zone between the head and the container, i.e. the sealing area. In fact, such area is very close to the front end of the piston, where the lubricant emitted by the lubricating bushing may not arrive.
- Since the lubricant does not reach the friction zone between the piston and the container in a targeted manner, an attempt is made to improve the sliding of the piston by injecting a high amount of lubricant, much more than what would be needed if the piston could be lubricated in the sealing area.
- Such a extensive use of lubricant away from the head also results in lubricant flowing out from the container.
- Since the lubricant is injected by the lubrication nozzles into an area which, being distant from the piston head, does not undergo the same cooling as the head, the lubricant undergoes a phase change to a gaseous state, losing efficiency and generating fumes that must be aspirated.
- In the case of containers provided with an intake duct for putting them in a vacuum, the presence of gaseous lubricant in the container causes the lubricant to be sucked out of the duct rather than deposited on the piston.
- To attempt to overcome such drawbacks, pistons having lubrication holes leading to the vicinity of the head in the sealing area with the container have been proposed. Examples of such pistons are described in
DE3913494A1 ,JP2009279645A DE29721722U1 ,JP2010269319A - Ultimately, the piston with the lubricating bushing is complex to construct and requires frequent maintenance, especially to remedy the breakage or obstruction of the tubes and the lubrication nozzles.
- The object of the present invention is to propose a piston for a die-casting machine to overcome the drawbacks mentioned above with respect to the pistons according to the prior art.
- Such objects are achieved by a piston according to
claim 1. - The features and advantages of the piston according to the present invention will be apparent from the following description, given by way of non-limiting example, of its preferred embodiments according to the appended drawings. In said drawings:
-
figure 1 shows a piston according to the invention, in a first embodiment, in a perspective view; -
figure 2 is a side view of the piston; -
figure 3 is an axial section of the piston along the line A-A offigure 2 ; -
figure 4 shows the piston inserted into a container of a press of a die-casting machine; -
figure 5 is a perspective view of only the piston's stem; -
figure 6 is a side view of the stem; -
figure 7 is an axial section of the stem along the line A-A infigure 6 ; -
figure 8 is another side view of the stem; -
figure 9 is an axial section of the stem along the line A-A infigure 8 ; -
figure 10 is a cross-sectional view of the stem along the line B-B infigure 8 ; -
figure 11 is an enlarged side view of the distal end of the stem; -
figure 12 is a cross-sectional view of the end of the stem along the line D-D infigure 11 ; -
figure 13 is another enlarged side view of the distal end of the stem; -
figure 14 is an axial sectional view of the end of the stem along the line C-C infigure 13 ; -
figure 15 is a cross-sectional view of the end of the stem along the line E-E infigure 13 ; -
figure 16 is an axial section of a piston in a variant embodiment, without a sealing ring; -
figure 17 is an axial section of the piston offigure 16 provided with a sealing ring; -
figures 17a and 17b are two further axial sections of the piston offigure 16 ; -
figure 18 is an axial section of only the piston head offigure 17 , wherein the metal penetrating below the sealing ring is shown; -
figure 18a is an enlarged view of the detail B circled infigure 21 ; -
figures 19, 20, 21 show, in perspective, a side and axial cross-sectional view, respectively, of an axial pin for supporting the piston head; -
figure 22 is an axial section of a piston in a variant embodiment; and -
figures 23 and23a are two axial sections of a piston in a further embodiment. - In the following description, whenever possible, some elements common to the various embodiments of the invention are indicated at the same numeric references.
- Moreover, unless expressly indicated otherwise, elements described for one embodiment of a piston may be present, optionally adapted as required, also in other described embodiments of a piston.
- With reference to the attached figures, at 1; 500; 700 a piston of a press of a die-casting machine, in particular of the cold chamber type, is shown. The press comprises a
container 400 wherein thepiston 1; 500; 700, or at least one of its terminal parts for pushing the molten metal, is housed slidably. Thecontainer 400 has, in its upper part and at its end, a loading hole for molten metal, e.g., aluminum. At the end opposite to said loading hole, thecontainer 400 has slits 402 to which correspond starting points of casting branches that flow into a die. Thepiston 1; 500; 700 is thus axially slidable inside thecontainer 400 to push the metal fed through the loading hole into the casting branches and then into the die. - The
piston 1; 500; 700 comprises astem 10; 510; 710 extending between aproximal end 11, either rearward with respect to the piston feed direction in the container and adistal end 12; 512; 712, or forward, along a piston axis X. - The
piston 1; 500 terminates with apiston head 50; 550; 750 extending from the distal end of the stem and has a side wall with at least onesealing area 52; 552; 752 suitable to form a seal on the wall of saidcontainer 400 of the press. - The
piston 1; 500; 700 is provided with a lubrication circuit adapted to facilitate the sliding of the piston in thecontainer 400. - Said lubrication circuit comprises
first lubrication ducts stem 10; 510; 710 and terminating at thedistal end 12; 512; 712 of said stem, andsecond ducts 20 made in thepiston head 50; 550; 750, communicating fluidically with said first ducts and flowing into the side wall corresponding at least to saidsealing area 52; 552; 752. - In an embodiment illustrated in
figures 1 to 15 , the first lubrication ducts comprise afeed duct 14 extending longitudinally from alubricant inlet hole 15 and branching into at least twodistribution ducts 18 angularly equidistant from the piston axis X. - The
second lubrication ducts 20 are a continuation of saiddistribution ducts 18. In other words, the terminal end of eachdistribution duct 18 is in direct communication with the initial end of a correspondingsecond lubrication duct 20. - In a preferred embodiment, the
inlet hole 15 for the lubricant is made near theproximal end 11 of thestem 10. Thefeed duct 14 thus extends almost over the entire length of the stem, parallel to the piston axis X and lateral with respect to an axial cooling duct, which will be described below, ending near thedistal end 12. As may be seen in particular infigure 3 , also thedistribution ducts 18, made in thedistal end portion 12 of thestem 10, extend parallel to the piston axis X. Thefeed duct 14 and thedistribution ducts 18 are connected to each other by branchingducts 16 extending from the end of thefeed duct 14 in a transverse direction with respect to the piston axis X. - In a preferred embodiment, the
piston head 50; 550; 750 has at least one sealingring 60 housed in arespective ring seat 62. Examples of piston heads with sealing ring to which the teaching of the present invention may be applied are described inWO2007116426A1 andWO2009125437A1 in the name of the same applicant. - The
ring seat 62 is formed by an annular recess made in the lateral surface of the piston head. Saidring seat 62 is radially delimited by a bottom 62' and axially at least by arear edge 62a, preferably also by afront edge 62b located near thefront face 602 of the piston head. - For example, the bottom of the sealing
ring seat 62 may advantageously be connected to thefront surface 602 of the piston head through connectingchannels 604 so that the molten metal present in the container may flow under the ring and, solidifying, create a progressive thickening that causes the ring to enlarge radially, compensating for its wear and ensuring the sealing effect over time. It should be noted that, in one embodiment, the sealingring 60 has a longitudinal gap 60', e.g., in the form of a step, which allows it to expand radially. - In accordance with an aspect of the invention, the
second lubrication ducts 20 flow at least into thering seat 62 below the same. At the open end of saidsecond ducts 20, the sealing ring is closed. Therefore, saidsecond ducts 20 are covered, and thus protected, by the sealingring 60 against possible obstructions by the metal that should penetrate between the piston and thecontainer 400. - The pressurized lubricant is then forced to infiltrate under the sealing ring and out of the piston through the gaps between the sealing
ring 60 and the piston head and/or through the longitudinal slit 60' of the sealingring 60. - In particular, the pressurized lubricant is forced to flow out of the piston through the gaps between the sealing
ring 60 and theedges ring seat 62. - To this end, the sealing
ring 60 is housed with some play in therespective ring seat 62. 'Housed with play' is intended to mean that the sealingring 60 is not engaged in a forced manner in therespective ring seat 62 but rather that between the sealingring 60 and eachedge ring seat 62 there is a certain and calibrated gap, e.g., 0.1 mm or less. - With such play or gap, the pressurized lubricant, e.g., at 200 bar, may pass between the sealing
ring 60 and theedges ring seat 62, while the metal, even if when in liquid state, may not pass. - It should be noted that the expansion of the lubricant below the sealing
ring 60 along the full circumference of thering seat 62 is made possible and facilitated not only by the high pressure to which the lubricant is subjected but also by the elasticity of the sealingring 60, due to the presence of the longitudinal slit 60'. - Thus, at least a double effect is achieved: the lubricant, flowing out from the gaps between the ring and the edges of the seat, acts precisely in the contact area between the piston and the inner surface of the container, i.e. the area of the sealing
ring 60; moreover, flowing onto the bottom of thering seat 62, the lubricant contributes to the radial expansion of the ring when the same begins to wear out. - It should be noted that, since the outlet passage of the lubricant is made at least of the circular gaps between the sealing
ring 60 and theedges ring seat 62, even if a certain amount of metal in the liquid state could penetrate between the piston head and the container, it is very unlikely that such amount of metal would be distributed precisely around the entire circumference of the gap between the sealingring 60 and therear edge 62a of thering seat 62. Therefore, contrary to the pistons of the prior art, it is practically impossible for the metal to seal completely all the gaps between the sealing ring and the piston head and thus prevent the lubricant from escaping. - In a preferred embodiment, wherein the bottom 62' of the
seat 62 of the sealing ring is connected with thefront surface 602 of the piston head through connectingchannels 604 for an inflow of metal under the sealingring 62, between the openings 604' of said connectingchannels 604 in the bottom 62' of thering seat 62 and therear edge 62a of saidseat 62, the sealingring 60 and thering seat 62 have interlocking orcomplementary coupling portions ring 60 and - during cooling and solidification - reaching the portion of thering seat 62 comprised between said interlocking coupling portions and therear edge 62a of theseat 62. In other words, the liquid metal that reaches thering seat 62 through the connectingchannels 604 is forced to solidify in the front portion of thering seat 62 between said labyrinth and thefront edge 62b (or, if saidfront edge 62b is not provided, between the labyrinth and thefront surface 602 of the piston head). - In an embodiment illustrated in
figures 1-15 , said interlocking coupling portions comprise one or a pair ofannular ribs 606 extending from the bottom 62' of thering seat 62 and correspondingannular grooves 608 made in the inner wall of the sealingring 60. - Conversely, in the variant embodiment illustrated in
figures 16-18 and23 , the bottom 62' of thering seat 62 is grooved by anannular groove 606 wherein arib 608 engages extending from the inner wall of the sealingring 60. - In a preferred embodiment of the piston, in the bottom 62' of the
band seat 62, in an advanced position with respect to the portions of interlocking coupling portions, anannular channel 610 is made, suitable to receive the metal coming from theconnection channel 604. -
Figure 18a shows schematically the deposit of metal M in the front portion of thering seat 62, under the sealingring 60, and particularly in theannular channel 610. - In the embodiments described above, the
second lubrication duct 20 which flows under the sealing ring flows into the rear portion of thering seat 62 between the interlockingcoupling portions rear edge 62a of thering seat 62. Thus, saidsecond duct 20 is protected, by means of the labyrinth formed by the interlocking coupling portions, from any obstruction caused by the penetration of the liquid metal under the sealingring 60. It should be noted that, while the liquid metal which penetrates under the sealingring 60 cannot pass through the labyrinth, due to its density, pressure and the fact that it tends to solidify as it cools, the lubricant has a density and a pressure making it able to creep between the interlockingcoupling portions front edge 62b, although most of the lubricant flows out through the gap between the ring and therear edge 62a, finding no obstacle in this case. - Since the lubricant reaches in a targeted way the area of greatest friction between the piston and the container, the amount of lubricant necessary to ensure the proper sliding of the piston is considerably less than that used in the pistons of the prior art, where the lubricant fails to reach the area of the sealing ring.
- It should furthermore be noted that since the sealing
ring 60 is positioned close to the front end of the piston, the possible presence of suction means, provided in the intermediate or rear position, to put the chamber of the container in a vacuum, does not have a significant influence on the action of the lubricant. - In a preferred embodiment, the
second ducts 20 have a first section 20' parallel to the piston axis X and at least a secondradial section 20" flowing at least in thering seat 62. - According to one embodiment, the
piston head 50; 550; 750 is removably connected to thestem 10; 510; 710. Between the stem and the head there are provided sealed fluidic connection means 4; 560 between thefirst lubrication ducts second lubrication ducts 20. - In an embodiment shown in
figures 1-21 , thedistal end 12 of thestem 10 is flanged so as to allow an axial juxtaposition between thestem 10 and thepiston head 50. In this case, the sealed fluidic connection meanscomprise connection bushings 4, each inserted with calibrated interference half in a terminal section of afirst lubrication duct 18 and the other half in the initial section of asecond lubrication duct 20. Each of said halves is fitted with anannular sealing element 61. - In one embodiment, the flanged
distal end 12 of thestem 10 and the adjacent end of thepiston head 50 are connected by means of screws 12' (shown infigure 17b ). To this end, in the lateral surface of thedistal end 12 of thestem 10, a plurality ofradial recesses 22 are formed, for example, angularly equidistant and semicircular, which allow access to corresponding screw holes 24 made in said flangeddistal end 12, parallel to the piston axis X, and facing corresponding screw holes 24'-visible in the view offigure 17b - made in thepiston head 50. By means of said radial recesses 22, it is then possible to screw/unscrew the screws 12' of the stem on the piston head. - Therefore, advantageously, in the piston assembly stages, it is sufficient to insert the
fluidic connection bushings 4 in the ends of thelubrication ducts - The piston according to the embodiment illustrated in
figures 16-18 has a structure similar to the one described for the piston offigures 1-15 and differs from the latter only in having a singlefirst lubrication duct 14 extending into thestem 10 and a singlesecond lubrication duct 20 aligned with thefirst lubrication duct 14 extending into the piston head and comprising, as described above, a first longitudinal section 20' and a secondradial section 20" flowing into thering seat 62. - In a preferred embodiment, the
piston 1; 500 is suitable for use in cold chamber die-casting machines. To this end, in the stem and in the piston head, a cooling circuit is made, suitable to circulate a cooling fluid inside the piston head. - In an advantageous embodiment, the
piston head 50 comprises a hollowouter body 64 fitted, e.g., in the form of a cap, on anaxial support pin 66; 766. In an embodiment illustrated infigures 1-21 , saidaxial support pin 66 has a proximal orrear end 67, engaging in a correspondingaxial recess 68 made in thedistal end 12 of thestem 10. - Advantageously, between the outer
hollow body 64 and thepin 66 there is no play, at least between the respective side walls. In other words, the outerhollow body 64 cannot move radially with respect to pin 66. Similarly, also theproximal end 67 of thepin 66 is inserted with calibrated interference, i.e. without play, in the correspondingaxial recess 68. - Such a solution allows, together with the screwing of the head onto the stem by means of screws distributed along a circular crown, to achieve and maintain over time a perfect coaxiality between the piston head and the stem. In other words, the
support pin 66, partially penetrating the inside of the stem, acts as a means of guidance and axial support for thepiston head 50. - In one embodiment, the
stem 10 and thepin 66 have respective and aligned axial cooling holes 70, 72 wherein adelivery tube 74 for a cooling fluid is inserted. Saiddelivery tube 74 communicates with the outside through aninlet hole 80 for the cooling fluid, e.g., made radially in the stem near thedistal end 12, and flows onto thefront surface 76 of theaxial pin 66. Saidfront surface 76 is in fluidic communication, e.g., through a plurality ofhelical ducts 77, with aspiral cooling channel 78 formed in the outer lateral surface of theaxial pin 66. Saidspiral cooling channel 78 then circulates the cooling fluid around and over the entire outer surface of theaxial pin 66 in contact with the outerhollow body 76, cooling it down. The coolingchannel 78 flows into areturn duct 82 communicating with anoutlet hole 84 for the cooling fluid, made in the stem. - In one embodiment, said
return duct 82 is formed by an annular space between theaxial cooling hole delivery tube 74 of the cooling fluid. For example, thereturn duct 82 communicates with thespiral cooling channel 78 through one or moreradial holes 83 made in theaxial pin 66. - It is to be noted that, in a preferred embodiment, the longitudinal lubrication holes 14 and cooling holes 70 made in the
stem 10 are obtained by machining carried out on the rear side of thestem 10. Therefore, in order to close such holes on said side, theproximal end 11 of thestem 10 comprises acap 90. - In one variant embodiment of a
piston 500 illustrated infigure 22 , thedistal end 512 of thestem 510 and thepiston head 550 have respective spherical coupling surfaces 514, 554 so as to realize an articulated joint between the stem and the piston head. In this embodiment, sealed fluidic connection means compriseball joints 560, each having a firstspherical end 561 inserted in a terminal portion of a respectivefirst lubrication duct 14 and a secondspherical end 562 inserted in an initial section of a respectivesecond lubrication duct 20, each of said spherical ends being provided with an annular sealing element. - In one embodiment, the
piston head 550 is held in contact with thestem 510 by means of a connectingcap 570 fixed to the stem. For example, said connectingcap 570 has anengagement end portion 572 at the front which forms an undercut wherein a rear step-shapedportion 574 of thepiston head 550 engages. - In a further variant embodiment of a
piston 700 illustrated infigures 23 and23a , thepiston head 750 is connected to thestem 710 via an articulated joint 800. Said articulated joint 800 allows thehead 750 to make deviations of a few degrees with respect to the piston axis X, and hence with respect to thestem 710, e.g., to allow it to slide into a non-perfectlyrectilinear container 400. - The articulated joint 800 has a
rear portion 810 coupled to thestem 810 and aspherical head 814 whereon thepiston head 750 is assembled. Therear portion 810 is fixed axially and radially to thestem 710, e.g., by means of radial blocks 812. - For its assembly on the
spherical head 814, thepiston head 750 comprises arear flange 820 surrounding the rear portion of thespherical head 814 and which is removably secured, e.g., by means of screws, to a rear portion of thepin 766 surrounding the front portion of thespherical head 814. - Moreover, preferably, the
rear flange 820, and hence theentire piston head 750, is angularly fixed to the articulated joint 800, i.e. it is prevented from rotating about the piston axis X, e.g., by means of aspline 816. Thus, thesecond lubrication duct 20, and in particular theend section 20", is always turned in the desired direction, normally upwards. In fact, the piston is thus lubricated by the lubricant running from top to bottom; moreover, the metal in the liquid state is less likely to solidify on the upper, hotter part of the piston. - In this embodiment, the
piston head 750 being spaced from thestem 710, thefirst lubrication duct 14, made in thestem 710, is fluidically connected to thesecond lubrication duct 20, made in thepiston head 750, by means of a connectingtube 714. Preferably, said connectingtube 714 has a spiral shape or is, in any case, suitable to allow displacements of thepiston head 750 with respect to thestem 710. - The portions of the
second lubrication duct 20 made in therear flange 820, in thepin 766, and in thehollow body 64 are connected to each other through theconnection bushings 4. - In a preferred embodiment, along the lubrication circuit, e.g., in the
first lubrication duct 14, there is provided at least onenon-return valve 5 adapted to ensure the unidirectionality of the flow of lubricant from the stem to the piston head.
Claims (10)
- A piston for a die-casting machine, in particular a cold chamber die-casting machine, where said machine comprises a press with a container in which the piston is housed so as to slide, the piston comprising,- a stem extending from a proximal end to a distal end along a piston axis;- a piston head which is removably connected to the distal end of the stem and has a side wall with at least one sealing area suitable to form a seal on the wall of said container of the press; and- a lubrication circuit suitable to facilitate the sliding of the piston in said container and comprising:- at least one first lubrication duct made in the stem and ending at the distal end of said stem, and- at least one second duct made in the piston head, fluidically communicating with said first duct and flowing into the lateral wall at least corresponding to said sealing area,wherein sealed fluidic connection means between said first lubrication duct and said second lubrication duct are provided between said stem and head, said sealed fluidic connection means comprising a connection bushing inserted with calibrated interference one half in a terminal section of the first lubrication duct and the other half in an initial section of the second lubrication duct.
- A piston according to the preceding claim, wherein each of said halves is fitted with an annular sealing element.
- A piston according to claim 1 or 2, wherein said sealing area is provided with at least one sealing ring housed in a respective ring seat formed in the side wall of the head, said sealing ring being longitudinally interrupted by a longitudinal slit permitting the radial expansion of the sealing ring, and wherein the second lubrication duct flows into said ring seat under said sealing ring, said second duct being covered by the sealing ring, such that the lubricant flows out from the piston head through the gaps between the sealing ring and the piston head and/or through said longitudinal slit.
- A piston according to claim 3, wherein said gaps comprise at least the gap between the sealing ring and the rear edge that delimits the ring seat posteriorly.
- A piston according to claim 3 or 4, wherein said gaps have a width of 0.1 mm or less.
- A piston according to any one of the claims 3-5, wherein the bottom of the ring seat is connected to the front surface of the piston head through connecting channels for a metal influx under the sealing ring, and wherein between the apertures of said connecting channels at the bottom of the ring seat and the rear edge of said seat, the sealing ring and the ring seat have interlocking coupling portions adapted to stop the passage of metal in the liquid state from penetrating below the sealing ring.
- A piston according to the preceding claim, wherein said second lubrication duct flows into the rear portion of the ring seat comprised between said interlocking coupling portions and the rear edge of the ring seat.
- A piston according to any of the preceding claims, wherein the first lubrication ducts comprise a feed duct which extends longitudinally from a lubricant inlet hole and which branches into at least two distribution ducts angularly equidistant in relation to the piston axis, the second lubrication ducts being a continuation of said distribution ducts.
- Piston according to any of the claims 3-8, wherein said second ducts have a first section parallel to the piston axis and at least one second radial section flowing into the ring seat.
- A piston according to any one of the preceding claims, wherein a cooling circuit is made in the stem and in the piston head suitable to circulate a cooling fluid inside the piston head.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SI201231866T SI3266538T1 (en) | 2011-06-28 | 2012-06-27 | Piston for a die-casting maching |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT000095A ITBS20110095A1 (en) | 2011-06-28 | 2011-06-28 | PISTON FOR A DIE CASTING MACHINE |
EP12745551.7A EP2726233B1 (en) | 2011-06-28 | 2012-06-27 | Piston for a die-casting machine |
PCT/IB2012/053256 WO2013001469A1 (en) | 2011-06-28 | 2012-06-27 | Piston for a die-casting machine |
Related Parent Applications (1)
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EP12745551.7A Division EP2726233B1 (en) | 2011-06-28 | 2012-06-27 | Piston for a die-casting machine |
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EP3266538A1 true EP3266538A1 (en) | 2018-01-10 |
EP3266538B1 EP3266538B1 (en) | 2020-12-02 |
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EP17179726.9A Active EP3266538B1 (en) | 2011-06-28 | 2012-06-27 | Piston for a die-casting maching |
EP12745551.7A Active EP2726233B1 (en) | 2011-06-28 | 2012-06-27 | Piston for a die-casting machine |
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EP12745551.7A Active EP2726233B1 (en) | 2011-06-28 | 2012-06-27 | Piston for a die-casting machine |
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US (1) | US9523430B2 (en) |
EP (2) | EP3266538B1 (en) |
JP (1) | JP6033858B2 (en) |
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Also Published As
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SI3266538T1 (en) | 2021-02-26 |
US9523430B2 (en) | 2016-12-20 |
CA2838549C (en) | 2019-09-10 |
CN103648688A (en) | 2014-03-19 |
RU2589647C2 (en) | 2016-07-10 |
BR112013033310A2 (en) | 2017-07-04 |
EP2726233B1 (en) | 2017-07-12 |
ES2839504T3 (en) | 2021-07-05 |
BR112013033310B1 (en) | 2022-09-20 |
JP6033858B2 (en) | 2016-11-30 |
EP3266538B1 (en) | 2020-12-02 |
CN103648688B (en) | 2016-01-20 |
JP2014518161A (en) | 2014-07-28 |
ES2643390T3 (en) | 2017-11-22 |
RU2013157153A (en) | 2015-06-27 |
CA2838549A1 (en) | 2013-01-03 |
ITBS20110095A1 (en) | 2012-12-29 |
PL2726233T3 (en) | 2017-11-30 |
EP2726233A1 (en) | 2014-05-07 |
WO2013001469A1 (en) | 2013-01-03 |
US20140123848A1 (en) | 2014-05-08 |
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